Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B19/00—Engines characterised by precombustion chambers
  • F02B19/06—Engines characterised by precombustion chambers with auxiliary piston in chamber for transferring ignited charge to cylinder space
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
  • F02B75/18—Multi-cylinder engines
  • F02B75/20—Multi-cylinder engines with cylinders all in one line
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D15/00—Varying compression ratio
  • F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
  • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
  • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B75/00—Other engines
  • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
  • F02B75/18—Multi-cylinder engines
  • F02B2075/1804—Number of cylinders
  • F02B2075/1812—Number of cylinders three
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
  • F02B2275/20—SOHC [Single overhead camshaft]
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B3/00—Engines characterised by air compression and subsequent fuel addition
  • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the present invention relates to an internal combustion engine by self-ignition as described in Luxembourg patent No. 86 506 for a mixed combustion cycle engine with controlled ignition, which comprises an axial grouping of the three cylinders joined in a triangle allowing parallel centralization of the two vile ⁇ brequins in the cylinder block.
• the object of the present invention relates to the means of producing an internal combustion engine by self-ignition which can operate at low compression rate and high supercharging rate. These means allow the introduction into the cylinder of a larger amount of air allowing the combustion of a higher weight of fuel without increasing the maximum temperature; from these means an increase in the average pressure results without having to increase the maximum pressure. Means for starting and operating the engine are also provided without the addition of a boost pressure.
• each cylinder has a corresponding piston, the first piston moving in the first cylinder used for the admissions, compression, expansion and exhaust phases, this first piston dependent, via a connecting rod, from the first crankshaft located in the cylinder block.
• the second piston moving in the second cylinder delimiting the combustion prechamber where there is a glow plug and a fuel injector, this second piston depen ⁇ dant, via a connecting rod, the second crankshaft also located in the cylinder block.
• the first crankshaft is connected by a trans ⁇ mission to the second crankshaft via known means of the coupler member located either inside or outside the cy ⁇ lindre casing.
• the gas pedal acting by known means on the quantity of fuel to be injected into the combustion prechamber.
• the invention applies equally well to two or two cycle engines. four stroke.
• FIG. 1 is a partial view in two broken sections A-A of the transverse part of a two-stroke engine showing in the foreground a pair of gears performing, via the coupler, the transmission between the two crankshafts.
• FIG. 2 is a plan view of the joint plane of the cylin ⁇ dre housing connecting the cylinder head in two broken sections with parallel planes A-A.
• FIG. 3 is a plan view of the joint plane of the cylinder head re ⁇ connecting the cylinder block in two broken sections with parallel planes A-A.
• a motor which brings together, side by side, the first and second cylinders (2), (7), so that the latter are presented obliquely on the joint plane of the casing.
• cylinder (5) relative to the shaft lines of the two crankshafts (4) and (13).
• This arrangement has the advantage of allowing the enclosing of the planes of rotation of the two crankpins, so that the plane of rotation of the crank pin of the first crankshaft (4-) is inserted next to the plane of rotation of the crank pin of the second crankshaft (13).
• the lower orifices of the two cylinders (2), (7) serving as passage for their respective piston (1), (6) are located in the cylinder block (5), facing the two crankshafts respectively (4) and (13) and to the engine oil sump (14).
• This isolation has the advantage of reducing the distance between the two vile ⁇ brequins (4), (13), as well as that of the two cylinders (2), (7), which has the effect of reducing the size of the cylinder housing (5).
• the latter comprises means so that the transmission between the two vile ⁇ brequins (4) and (13) is effected by a pair of gears (15) and (16) forming part of the cylinder block (5); the first gear (15), centered on the output shaft of the first crankshaft (4), drives the second gear (16) in rotation.
• the axis of transmission of the input gear of the cage of the coupler becomes integral with the axis (17) of the second gear (16), while the transmission axis of the output gear of the cage of the de ⁇ coupler comes integral with the output axis of the second crankshaft (13), so that the two crankshafts (4) and (13) form a cine ⁇ matic chain at the same speed of rotation in which the coupler and the coupler means are also located to allow the angular phase shift between the shafts of the two crankshafts (4) and (13).
• the four-stroke engine can also be provided with a kinematic chain where the crankshaft (13) is at half speed of the crankshaft (4).
• the setting is carried out so that the carriage ( 34) of the coupler occupies the first limit for stopping the axial sliding of the carriage (34) (in position D, FIG. 4).
• the input axis (36) longer than the output axis (37) of the coupler is connected to the axis of the second gear (16) with the position of the piston (1) of the first cylinder ( 2) located at top dead center, at the end of compression phase.
• the output axis (37) of the coupler is connected to the axis of the second city- brequin (13) when the piston (6) of the second cylinder (7) is located
• means are provided for synchronizing and automating the axial movement of the carriage (34) of the coupler as a function of the boost pressure (FIG. 4).
• a pneumatic cylinder (30) is connected by a pipe (31) to the supercharging pipe (32) between the engine and the turbocharger (9).
• the pneumatic cylinder (30) ( Figure 4) is equipped with a piston under tension of a calibrated spring, said piston communicating outside the cylinder (30) by an axis (33) integral with the carriage (34) of the coupler, so that the boost pressure in the cylinder (30) can act on the piston and the carriage (34) of the coupler, until the contraction of the calibrated spring balances the boost pressure.
• means are also provided for varying the stop of the injection pump determining the maximum flow rate of the current with respect to the engine's volumetric ratio.
• the abovementioned abutment is connected to the axis of the pneumatic piston (33) which is integral with the carriage (34) of the coupler by means either mechanical, electrical or other, in such a way that the displacements of the pneumatic piston generated by the supercharging pressures fas ⁇ simultaneously vary the volumetric ratio and said stop. The latter is adjusted to allow an increase in the maximum fuel flow in proportion to the reduction in the volumetric ratio.
• each cylinder is formed of two elements (18) and (19).
• the first elements (18) of the cylinders (2), (7), open at both ends, are either bored directly in the cylinder block (5), or designed in sleeves added to be received in appropriate housings of the cylinder block ( 5), the seal being produced by the support of a flange at the top of the liners, in a housing provided at the joint plane (24) of the cylinder casing (5);
• the second elements (19) of the cylinders (2), (7), closed at the end opposite to the junction of the two elements (18,19) are either bored directly in the cylinder head (20), or designed in inserts to be received in appropriate housings of the cylinder head (20), the seal being produced by the support of a flange at the bottom of the liners, in a housing provided at the joint plane (23) of the cylinder head (20).
• the liners of the cylinder block (5) and the cylinder head (20) can also be designed in one piece.
• the rotation of the first crankshaft (4) ensures that the first piston (1) reciprocates in the mier and second elements (18 and 19) of the first cylinder (2).
• the rotation of the second crankshaft (13) ensures an alternative movement of the piston (6) in the first and second elements (18,19) of the second cylinder (7).
• the bottom of the second element (19) of the first cylinder (2) comprises an exhaust pipe (29) arranged in the cylinder head (20), putting in communication, via the two valves (26), ( 26 '), the cylinder (2).
• the valves are actuated by a camshaft (27) and driven at the same speed of rotation by one of the two crankshafts (4) or (13).
• Inlet lights (28) are arranged on the periphery of the first cylinder (2), so that they are uncovered or masked by the first piston (1) of the first cylinder (2).
• the space freed from the cylinder head (20) makes it possible to release a first orifice for the glow plug (10) and a second orifice for the fuel injector. fuel (11) ( Figure 3).
• means are provided for positioning the two crankshafts (4), (13) located in the cylinder block (5), so as to cause the heads of the two pistons to emerge cyclically (1), (6 ), without their segmentation (21), beyond the first elements (18) of the two cylinders (2), (7) of the cylinder block (5), the emergence of the heads of the two pistons (1), (6) corresponding with the space reserved for the second elements (19) of the two cylinders (2), (7) of the cylinder head (20).
• the communication channel (22) is provided with a wide section connection to facilitate massive transfers of the high frequency fluid between the two cylinders (2), (7) in the compression, combustion and gas expansion phases.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Output Control And Ontrol Of Special Type Engine (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=19730975

Family Applications (1)

Country Status (8)

Cited By (2)

Families Citing this family (11)

Citations (5)

Family Cites Families (10)

• 1987
  • 1987-10-16 LU LU87021A patent/LU87021A1/fr unknown
• 1988
  • 1988-10-12 US US07/368,317 patent/US4998511A/en not_active Expired - Fee Related
  • 1988-10-14 EP EP88908760A patent/EP0351420B1/de not_active Expired - Lifetime
  • 1988-10-14 JP JP63508049A patent/JPH02501843A/ja active Pending
  • 1988-10-14 ES ES8803118A patent/ES2012860A6/es not_active Expired - Lifetime
  • 1988-10-14 WO PCT/LU1988/000001 patent/WO1989003476A1/fr active IP Right Grant
  • 1988-10-14 CA CA000580233A patent/CA1304691C/fr not_active Expired - Lifetime
  • 1988-10-14 DE DE8888908760T patent/DE3872517D1/de not_active Expired - Lifetime

Patent Citations (5)

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